ADJUSTMENT MECHANISM FOR DISC BRAKE, WITH IMPROVED OVER-TORQUE CLUTCH

Description

BACKGROUND OF THE INVENTION

[0001] This invention relates to an adjustment mechanism for a disc brake as defined in claim 1 and to a disc brake as defined in claim 14.

[0002] Disc brakes are utilized to apply braking force to vehicles. In one known type of disc brake, an eccentric member rotates upon receiving an actuation force from a disc brake control. When the eccentric mechanism rotates it drives a sleeve to bring the backing plate and an associated friction surface into contact with a rotating disc.

[0003] With wear, the friction material begins to be spaced further from the disc. The prior art has proposed adjustment mechanisms which move the friction material closer to the wheel hub with wear. In one known adjustment mechanism, rotation of the eccentric member also rotates an adjustment member. The adjustment member in turn rotates an outer clutch member. The outer clutch member is connected to an inner clutch member through an over-torque connection. The inner clutch member is associated with a central gear through a one way clutch. The central gear in turn drives a gear transmission, which drives adjustment sleeves. The adjustment sleeves turn structure which advances the friction material closer to the rotating disc. In this way, when the eccentric member is rotated, the friction material is brought forwardly to accommodate wear.

[0004] The over-torque clutch insures that the friction material is not advanced to an undesirable extent. Once the friction material is in contact with the rotating disc, further advancement of the friction material would be undesirable. If the friction material is advanced further while in contact with the rotating hub, the torque load on the over-torque clutch exceeds the predetermined torque load. The clutch then allows relative movement and prevents further advancement of the friction material. In this way, undesirable advancement of the friction material due to the adjustment mechanism is avoided. When the eccentric member is released and returns to a non-braking position, the one-way clutch allows the return without further advancement. The structure described to this point is known.

[0005] In EP-A-0 703 380, a disc brake is shown which uses two levers for transforming the rotating movement of the eccentric into a rotating movement of the adjusting piston. A first lever is mounted on the eccentric and engages into the second lever. The second lever drives an adjusting gear, which engages the adjusting piston.

SUMMARY OF THE INVENTION

[0006] In a disclosed embodiment of this invention, an improvement to the over-torque mechanisms described above includes a plurality of members axially biased to connect the inner and outer over-torque members for rotation. Should the load on this connection exceed a predetermined torque limit, then the members move to allow the inner and outer over-torque members to rotate relative to each other

[0007] In one preferred embodiment of this invention, the members are balls spring biased by a spring to be received in openings in both of inner and outer over-torque members. Since the balls are actually received in the openings, it is not a friction force which connects the inner and outer over-torque clutch members. Instead, it is the presence of the balls themselves that transmit rotation between the inner and outer over-torque clutch members. This may provide more reliable rotation in certain circumstances. Further, this arrangement requires a smaller radial space for the over-torque connection.

[0008] Should the force between the inner and outer over-torque clutch members exceed the predetermined torque load, then the balls are forced outwardly of the holes to allow relative rotation between the members. In a preferred embodiment, the balls ride in holes formed in a radially outwardly extending disc in the inner over-torque clutch member. The spring selectively biases the balls into holes which are drilled in the outer over-torque clutch member. The outer over-torque clutch member holes preferably have an inner diameter which is somewhat less than the outer diameter of the balls. In this way, the balls are only partially received in the holes.

[0009] These and other features of the present invention can be best understood from the following specification and drawings, of which the following is a brief description.

BRIEF DESCRIPTION OF THE DRAWINGS

[0010] 

Figure 1 is a view of a disc brake system incorporating the inventive clutch.

Figure 2 shows details of the inventive clutch.

Figure 3A shows the inventive clutch in a position to transmit rotation.

Figure 3B shows the inventive clutch member having moved to allow relative rotation between the over-torque clutch members.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0011] A disc brake system 20 is illustrated in Figure 1. The disc brake system 20 as shown is disclosed in co-pending United States application nos. 08/747,141 and 08/747,139, which are co-owned by the assignee of the present invention. The inventive aspects of this Application relate to an improved clutch mechanism as will be disclosed below. However, a brief understanding of the operation of the brake system 20 is necessary to understand the function of the inventive clutch.

[0012] As shown, a backing plate 22 carries a friction material 24 into contact with a rotating member 26. Rotating member 26 is associated with a wheel which is to be braked by the disc brake system 20. By bringing friction material 24 into contact with member 26, the rotation of the wheel may be slowed.

[0013] To move the friction material 24 into contact with member 26, an eccentric member 28 is rotated. With rotation of eccentric member 28, a sleeve 30 is moved axially towards and away from member 26. With movement of sleeve 30, sleeves 32 are moved forwardly. As shown, threaded members 34 are threadably received at 36 within sleeves 32. When sleeves 32 move forwardly, they carry threaded members 34, and hence backing plate 22 and friction material 24 into contact with member 26.

[0014] To adjust the position of the friction material 24 for wear, gears 38 are fixed to rotate with sleeves 32. Idler gears 40 engage a central adjustment gear 42. An over-torque clutch 44 is shown for selectively driving central gear 42. When central gear 42 rotates, it rotates idler gears 40, and outer gears 38. When outer gears 38 rotate, sleeves 32 rotate, and the threaded connection 36 to threaded members 34 advances members 34, hence bringing friction material 24 closer to rotating member 26.

[0015] Figure 2 shows certain details of the clutch 44. As shown, a central bolt 46 includes a threaded connection 47 within a bore 48 in sleeve 30. By tightening the bolt 36 within the bore 48, a spring load provided by the over-torque connection to be described below can be adjusted. As shown, a head 50 of bolt 46 abuts the central gear 42. An inner sleeve portion 52 of the central gear 42 rotates about bolt 46. A one way clutch 54, which may be conventional, allows rotation in one direction between an inner over-torque clutch member 56 and inner portion 52 of the central gear 42. When the eccentric 28 is rotated to bring the friction material 24 into contact with member 26, rotation may be transmitted by the one way clutch 54. However, when the eccentric member returns to its non-actuated position, the one-way clutch 54 does not reverse the rotation of the member 52. In this way, once adjustment does occur, it is not reversed when the brake returns to its non-actuated position.

[0016] The inventive aspects of this Application relate to over-torque clutch 44 which is positioned radially outwardly of the one-way clutch 54. As shown, an inner over-torque clutch member 56 is positioned radially inwardly of a spring 58, which may be a wave spring. Spring 58 applies an axial bias force to a washer 60. Washer 60 abuts one end of a plurality of balls 62. Balls 62 slide within a plurality of bores 64 in a disc 66 which extends radially outwardly of a sleeve portion 67 of inner over-torque clutch member 56. Although only two balls 62 are shown, several additional balls are preferably spaced circumferentially. Balls 62 can move through the bores 64 under the influence of the spring 58. An outer over-torque clutch member 68 includes bores 70. The inner diameter of the bore 64 is slightly greater than the outer diameter of the ball 62 such that the ball 62 can slide through the bore 64 between the torque transmission position shown on the left hand side of Figure 2, and to a non-rotation transmission position shown on the right hand side.

[0017] Bores 70, on the other hand, have an inner diameter which is less than the outer diameter of balls 62. Thus, when the over-torque clutch members 68 and 56 are in a position wherein torque is to be transmitted, the balls 62 are forced into the bore 70, and abut an end face of the bore. The balls 62 are now received in both bores 70 and bore 64. The balls transmit rotation between the inner torque member 56 and the outer torque member 68. As shown, gear teeth 72 are formed at an outer peripheral surface of the outer torque member 68.

[0018] As shown in Figure 3A, and adjustment member 74 rotates with rotation of the eccentric member 28. Lever 76 is utilized to rotate the eccentric member 28 to actuate the brake. Rotation of adjustment member 74 drives gear teeth 72 to rotate outer over-torque clutch member 68. If the balls 62 remain in position shown to the left hand side of Figure 3A, this rotation then results in rotation of inner over-torque clutch member 56, and hence adjustment of the position of the members 34, as explained in greater detail above.

[0019] However, in the event that the friction material 24 is brought into contact with the member 26, and yet the entire rotation stroke of the eccentric member 28 has not yet occurred, further rotation of the adjustment mechanism would be undesirable. Once friction material 24 has contacted the member 26, there is resistance to further rotation of the members 68 and 56. This resistance results in a reaction force from the surfaces defining the bore 70 against the end faces of the ball 62. As long as the spring force 58 exceeds those reaction forces, balls 62 remain in bores 70, rotation is transmitted between the members 68 and 56, and the adjustment mechanism advances the friction material 24. This is the Figure 3A position.

[0020] However, as shown in Figure 3B when the reaction force between the surface which defines bore 70 and the end face of the ball 62 exceeds the spring force from spring 58, washer 60 moves against the spring force 58. Balls 62 move out of holes 70, and member 68 may rotate relative to member 56. The spring force may be adjusted by tightening or loosening bolt 44.

[0021] The use of the axial spring to apply the force to the balls results in a positive connection of the balls between members 68 and 56. In some applications this may be an improvement over the systems described above, wherein rotation is transmitted through frictional contact. Moreover, the use of the axial spring force results in less required radial space, which may be desirable in some applications.

[0022] Preferred embodiments of this invention have been disclosed, however, a worker of ordinary skill in the art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.

Claims

1. An adjustment mechanism for a disc brake assembly comprising:

a central gear (42) associated with outer gears (40) that are adapted to advance a backing plate (22) towards a rotating brake member (26) in response to rotational input from said central gear (42) to accommodate friction material wear; and

an over-torque clutch (44) operably coupled to said central gear (42), said over-torque clutch (44) including inner (56) and outer (68) over-torque members, balls (62) being forced into holes (70, 64) in both said inner (56) and outer (68) over-torque members by a spring (58) acting along an axis of rotation of said inner (56) and outer (68) over-torque members, rotation being transmitted between said inner (56) and outer (68) over-torque members when said balls (62) are received in said holes (70, 64) in both said inner (56) and outer (68) over-torque members, and said balls (62) being moveable out of said holes (70, 64) in at least one of said inner (56) and outer (68) over-torque members to allow said inner (56) and outer (68) over-torque members to rotate relative to each other such that rotation is not transmitted to said central gear (42).

2. An adjustment mechanism as recited in Claim 1, wherein said inner over-torque member (56) includes a radially outwardly extending disc (66), said disc (66) including said holes (64), said balls (62) being received in said holes (64), said holes (64) in said inner over-torque clutch member (56) having an inner diameter which is slightly greater than an outer diameter of said balls (62), such that said balls (62) can move through said holes (64) and into said holes (70) in said outer over-torque member (68).

3. An adjustment mechanism as recited in Claim 2, wherein said holes (70) in said outer over-torque member (68) have an inner diameter which is less than an outer diameter of said balls (62), and such that said balls (62) are only partially forced into said holes (70) in said outer over-torque member (68).

4. A disc brake mechanism comprising:

backing plate (22) and friction material (24) which may be selectively moved toward and away from a member (26) to be stopped;

an actuation mechanism to be rotated, and to in turn move said backing plate (22) toward and away from the member (26) to be stopped;

and an adjustment mechanism according to any of the preceding claims.

5. A disc brake mechanism as recited in Claim 4, wherein an adjustment member, associated with said actuation mechanism, drives said outer over-torque member (68), and said balls (62) then transmit rotation to said inner over-torque member (56).

6. A disc brake mechanism as recited in Claim 4, wherein said balls (62) are spaced circumferentially about a central axis of said inner over-torque member (56), said balls transmitting rotation between said inner (56) and outer (68) over-torque members.

7. A disc brake mechanism as recited in Claim 6, wherein said holes (70) have an inner diameter which is less than an outer diameter of said balls (62) such that said balls (62) arc only partially forced into said holes (70) in said outer over-torque member (68).

8. A disc brake mechanism as recited in Claim 6, wherein said inner over-torque member (56) includes a radially outwardly extending disc (66), said disc (66) including said holes (64), and said balls (62) being received in said holes (64) in said disc (66), said holes (64) in said disc (66) having an inner diameter which is slightly greater than an outer diameter of said balls (62) such that said balls (62) can move through said holes (64) in said disc (66) and into holes (70) in said outer over-torque member (68).

9. A disc brake mechanism as recited in Claim 4, wherein a one-way clutch (54) is also positioned between said central gear (42) and said over-torque clutch (44).

10. A disc brake mechanism as recited in Claim 4, wherein said spring (58) provides an axial bias force.

11. A disc brake mechanism as recited in Claim 10, wherein said spring (58) biases a washer (60), said washer (60) biasing said balls (62) to retain said balls (62) in said holes (70, 64) in said inner (56) and outer (68) over-torque clutch member.

12. A disc brake mechanism as recited in Claim 4, wherein a bolt (46) is secured to a structure associated with said actuation mechanism, said structure not rotating with said over-torquc clutch (44), said bolt (46) including a head (50) providing a stop surface for a bias force provided by said spring such that the position of said bolt member (46) may be adjusted to adjust said bias force.

13. A disc brake mechanism as recited in Claim 12, wherein said spring (58) has one end abutting against said bolt head (50).

14. A disc brake mechanism as recited in Claim 13, wherein a second end of said spring (58) abuts a washer (60), said washer (60) forcing said balls (62) away from said bolt head (50) and into said holes (70, 64).

15. A disc brake mechanism as recited in Claim 14, wherein said balls are forced by said spring (58) into said holes (70, 64) in said inner (56) and outer (68) over-torque members.

Ansprüche

1. Nachstellmechanismus für eine Scheibenbremsbaugruppe, mit:

einem zentralen Zahnrad (42), das äußeren Zahnrädern (40) zugeordnet ist, die so ausgelegt sind, daß sie als Reaktion auf eine Eingangs-Rotationsenergie von dem zentralen Zahnrad (42) eine Grundplatte (22) in Richtung auf ein sich drehendes Bremselement (26) vorschieben, um einem Verschleiß des Reibmaterials Rechnung zu tragen; und

einer Überlastkupplung (44), die wirkungsmäßig an das zentrale Zahnrad (42) angeschlossen ist, wobei die Überlastkupplung (44) ein inneres (56) und ein äußeres (68) Überlastelement aufweist, wobei Kugeln (62) durch eine Feder (58), die längs einer Drehachse des inneren (56) und äußeren (68) Überlastelements wirkt, in Löcher (70, 64) sowohl in dem inneren (56) als auch dem äußeren (68) Überlastelement gedrückt werden, wobei zwischen dem inneren (56) und dem äußeren (68) Überlastelement eine Drehung übertragen wird, wenn die Kugeln (62) in den Löchern (70, 64) sowohl in dem inneren (56) als auch dem äußeren (68) Überlastelement aufgenommen sind, und wobei die Kugeln (62) aus den Löchern (70, 64) in dem inneren (56) und/oder dem äußeren (68) Überlastelement herausbewegt werden können, damit sich das innere (56) und das äußere (68) Überlastelement relativ zueinander so drehen können, daß die Drehung nicht auf das zentrale Zahnrad (42) übertragen wird.

2. Nachstellmechanismus nach Anspruch 1, bei dem das innere Überlastelement (56) eine sich radial nach außen erstreckende Scheibe (66) aufweist, wobei die Scheibe (66) die Löcher (64) aufweist, wobei die Kugeln (62) in den Löchern (64) aufgenommen sind, wobei die Löcher (64) in dem inneren Überlastkupplungselement (56) einen Innendurchmesser haben, der geringfügig größer als ein Außendurchmesser der Kugeln (62) ist, derart, daß sich die Kugeln (62) durch die Löcher (64) und in die Löcher (70) in dem äußeren Überlastelement (68) bewegen können.

3. Nachstellmechanismus nach Anspruch 2, bei dem die Löcher (70) in dem äußeren Überlastelement (68) einen Innendurchmesser haben, der geringer als ein Außendurchmesser der Kugeln (62) ist, und derart, daß die Kugeln (62) nur teilweise in die Löcher (70) in dem äußeren Überlastelement (68) gedrückt werden.

4. Scheibenbremsmechanismus mit:

einer Grundplatte (22) und einem Reibmaterial (24), die wahlweise auf ein anzuhaltendes Element (26) zu bzw. von diesem wegbewegt werden können;

einem zu drehenden Betätigungsmechanismus, der seinerseits die Grundplatte (22) auf das anzuhaltende Element (26) zu bzw. von diesem wegzubewegen hat;

und einem Nachstellmechanismus nach einem der vorhergehenden Ansprüche.

5. Scheibenbremsmechanismus nach Anspruch 4, bei dem ein dem Betätigungsmechanismus zugeordnetes Nachstellelement das äußere Überlastelement (68) antreibt und die Kugeln (62) dann eine Drehung auf das innere Überlastelement (56) übertragen.

6. Scheibenbremsmechanismus nach Anspruch 4, bei dem die Kugeln (62) um eine Mittelachse des inneren Überlastelements (56) umfangsmäßig beabstandet sind, wobei die Kugeln eine Drehung zwischen dem inneren (56) und dem äußeren (68) Überlastelement übertragen.

7. Scheibenbremsmechanismus nach Anspruch 6, bei dem die Löcher (70) einen Innendurchmesser haben, der geringer als ein Außendurchmesser der Kugeln (62) ist, derart, daß die Kugeln (62) nur teilweise in die Löcher (70) in dem äußeren Überlastelement (68) gedrückt werden.

8. Scheibenbremsmechanismus nach Anspruch 6, bei dem das innere Überlastelement (56) eine sich radial nach außen erstreckende Scheibe (66) aufweist, wobei die Scheibe (66) die Löcher (64) aufweist, und wobei die Kugeln (62) in den Löchern (64) in der Scheibe (66) aufgenommen sind, wobei die Löcher (64) in der Scheibe (66) einen Innendurchmesser haben, der geringfügig größer als ein Außendurchmesser der Kugeln (62) ist, derart, daß sich die Kugeln (62) durch die Löcher (64) in der Scheibe (66) und in die Löcher (70) in dem äußeren Überlastelement (68) bewegen können.

9. Scheibenbremsmechanismus nach Anspruch 4, bei dem ferner eine Freilaufkupplung (54) zwischen dem zentralen Zahnrad (42) und der Überlastkupplung (44) angeordnet ist.

10. Scheibenbremsmechanismus nach Anspruch 4, bei dem die Feder (58) eine axiale Vorspannkraft bereitstellt.

11. Scheibenbremsmechanismus nach Anspruch 10, bei dem die Feder (58) eine Scheibe (60) vorbelastet, wobei die Scheibe (60) die Kugeln (62) so vorbelastet, daß die Kugeln (62) in den Löchern (70, 64) in dem inneren (56) bzw. dem äußeren (68) Überlastkupplungselement gehalten werden.

12. Scheibenbremsmechanismus nach Anspruch 4, bei dem eine Schraube (46) an einer dem Betätigungsmechanismus zugeordneten Struktur befestigt ist, die sich nicht mit der Überlastkupplung (44) dreht, wobei die Schraube (46) einen Kopf (50) aufweist, der eine Anschlagfläche für eine von der Feder bereitgestellte Vorspannkraft bietet, derart, daß die Stellung des Schraubenelements (46) zur Regulierung der Vorspannkraft eingestellt werden kann.

13. Scheibenbremsmechanismus nach Anspruch 12, bei dem die Feder (58) mit einem Ende an dem Schraubenkopf (50) anliegt.

14. Scheibenbremsmechanismus nach Anspruch 13, bei dem ein zweites Ende der Feder (58) an einer Scheibe (60) anliegt, wobei die Scheibe (60) die Kugeln (62) von dem Schraubenkopf (50) weg und in die Löcher (70, 64) drückt.

15. Scheibenbremsmechanismus nach Anspruch 14, bei dem die Kugeln von der Feder (58) in die Löcher (70, 64) in dem inneren (56) bzw. dem äußeren (68) Überlastelement gedrückt werden.

Revendications

1. Un mécanisme d'ajustement pour un ensemble de frein à disque comprenant ;

une roue d'engrenage centrale (42) associée à des roues d'engrenage extérieures (40) destinées à faire avancer une plaque support (22) vers un élément de freinage rotatif (26) en réponse à une action de rotation venant de ladite roue d'engrenage centrale (42) pour compenser l'usure du matériau de friction ; et

un embrayage limiteur de couple (44) relié en fonctionnement à ladite roue d'engrenage centrale (42), ledit embrayage limiteur de couple (44) comprenant des éléments limiteurs de couple, intérieur (56) et extérieur (68), tandis que des billes (62) sont contraintes de pénétrer dans des passages (70, 64), ménagés dans les éléments limiteurs de couple, intérieur (56) et extérieur (68), par un ressort (58) agissant le long de l'axe de rotation desdits éléments limiteurs de couple, intérieur (56) et extérieur (68), la rotation se transmettant entre lesdits éléments limiteurs de couple, intérieur (56) et extérieur (68), lorsque lesdites billes (62) sont logées dans lesdits passages (70, 64) dans les éléments limiteurs de couple, intérieur (56) et extérieur (68), et lesdites billes (62) étant mobiles à l'extérieur desdits passages (70, 64) dans l'un au moins desdits éléments limiteurs de couple, intérieur (56) et extérieur (68), pour permettre auxdits éléments limiteurs de couple, intérieur (56) et extérieur (68), de tourner l'un par rapport à l'autre de sorte que cette rotation ne se transmette pas à la roue d'engrenage centrale (42).

2. Un mécanisme d'ajustement tel que décrit dans la revendication 1, dans lequel ledit élément de limiteur de couple (56) comprend un disque (66) s'étendant radialement vers l'extérieur, ledit disque comprenant lesdits passages (64), lesdites billes (62) étant introduites dans lesdits passages (64), lesdits passages (64), ménagés dans ledit élément d'embrayage limiteur de couple intérieur (56) ayant un diamètre intérieur légèrement supérieur au diamètre extérieur desdites billes (62), en sorte que lesdites billes (62) peuvent se déplacer à travers lesdits passages (64) et dans lesdits passages (70) desdits éléments extérieurs limiteurs de couple (68).

3. Un mécanisme d'ajustement tel que décrit dans la revendication 2, dans lequel
   lesdits passages (70) desdits éléments limiteurs de couple extérieurs (68) ont un diamètre intérieur inférieur au diamètre extérieur desdites billes (62) et tel que lesdites billes (62) sont seulement partiellement contraintes de pénétrer dans les passages (70) dudit élément extérieur limiteur de couple (68).

4. Un mécanisme de freinage à disque comprenant :

une plaque support (22) et un matériau de friction (24) pouvant être déplacé sélectivement pour se rapprocher et s'éloigner d'un élément (26) à arrêter ;

un mécanisme d'actionnement pouvant être mis en rotation, et pouvant à son tour déplacer ladite plaque support (22) pour la rapprocher et l'éloigner d'un élément (26) à arrêter ;

et un mécanisme d'ajustement selon l'une quelconque des revendications précédentes.

5. Un mécanisme de freinage à disque selon la revendication 4, dans lequel un élément d'ajustement associé audit mécanisme d'actionnement entraîne ledit élément extérieur limiteur de couple (68) et lesdites billes (62) puis transmet la rotation au dit élément intérieur limiteur de couple (56).

6. Un mécanisme de freinage à disque selon la revendication 4, dans lequel lesdites billes (62) sont réparties sur une circonférence autour d'un axe central dudit élément intérieur limiteur de couple (56), lesdites billes transmettant la rotation entre lesdits éléments limiteurs de couple intérieur (56) et extérieur (68).

7. Un mécanisme de freinage à disque selon la revendication 6, dans lequel lesdits passages (70) ont un diamètre intérieur inférieur au diamètre extérieur desdites billes (62) en sorte que lesdites billes (62) sont contraintes de pénétrer, seulement partiellement, dans lesdits passages (70) dans ledit élément extérieur limiteur de couple (68).

8. Un mécanisme de freinage à disque selon la revendication 6, dans lequel ledit élément intérieur limiteur de couple (56) comprend un disque (66) s'étendant radialement vers l'extérieur, ledit disque (66) comprenant lesdits passages (64), et lesdites billes (62) étant logées dans lesdits passages (64) dudit disque (66), lesdits passages (64) dudit disque (66), ayant un diamètre intérieur légèrement supérieur au diamètre extérieur desdites billes (62) en sorte que lesdites billes (62) peuvent se déplacer à travers lesdits passages (64) dudit disque (66) et à l'intérieur des passages (70) dudit élément extérieur limiteur de couple (68).

9. Un mécanisme de freinage à disque selon la revendication 4, dans lequel un embrayage unidirectionnel (54) est également positionné entre ladite zone d'engrenage centrale (42) et ledit embrayage limiteur de couple (44).

10. Un mécanisme de freinage à disque selon la revendication 4, dans lequel ledit ressort (58) exerce une force axiale de sollicitation.

11. Un mécanisme de freinage à disque selon la revendication 10, dans lequel ledit ressort (58) sollicite une rondelle (60), ladite rondelle sollicitant lesdites billes (62) pour retenir lesdites billes (62) dans lesdits passages (70, 64) dans ledit élément limiteur de couple intérieur (56) et extérieur (68).

12. Un mécanisme de freinage à disque selon la revendication 4, dans lequel un boulon (46) est fixé à une structure associée audit mécanisme d'actionnement, ladite structure ne tournant pas avec ledit embrayage limiteur de couple (44), ledit boulon (46) comprenant une tête (50) faisant fonction de surface d'arrêt pour une force de sollicitation exercée par ledit ressort en sorte que la position dudit élément de boulon (46) peut être ajustée de façon à régler ladite force de sollicitation.

13. Un mécanisme de freinage à disque selon la revendication 12, dans lequel l'une des extrémités dudit ressort (58) s'appuie sur ladite tête de boulon (50).

14. Un mécanisme de freinage à disque selon la revendication 13, dans lequel une seconde extrémité dudit ressort (58) bute contre une rondelle (60), ladite rondelle (60) repoussant lesdites billes (62) à distance de ladite tête de boulon (50) et dans lesdits passages (70, 64).

15. Un mécanisme de freinage à disque selon la revendication 14, dans lequel lesdites billes sont repoussées par ledit ressort (58) dans lesdits passages (70, 64) dans lesdits éléments limiteurs de couple intérieur (56) et extérieur (68).

Drawing